Heat exchanger, air conditioner, control method, controller and storage medium thereof

Abstract

The application provides a heat exchanger, an air conditioner and a control method, a controller and a storage medium thereof. The heat exchanger comprises a first heat exchange assembly, a second heat exchange assembly and a third heat exchange assembly. The gas-liquid separator comprises an input port, a gas phase outlet and a liquid phase outlet. The gas phase outlet is connected with the second heat exchange assembly through a first throttling device, and the liquid phase outlet is connected with the second heat exchange assembly. The first valve port, the second valve port, the third valve port and the fourth valve port of the first four-way valve are connected with the first heat exchange assembly, the third heat exchange assembly, the input port and the second heat exchange assembly respectively. The inlet of the one-way valve is connected with the second heat exchange assembly, and the outlet of the one-way valve is connected with the first heat exchange assembly. The embodiment of the application can improve the phenomenon that the performance of the heat exchanger is reduced due to excessive condensate liquid and evaporated gas, and can also realize the transformation of the number of flow paths in different heat exchange modes, so that the heat exchanger can run in a high-efficiency and stable state, thereby improving the performance of the air conditioner.

Description

Technical Field

[0001] This invention relates to the field of heat pump and air conditioning technology, and in particular to a heat exchanger, an air conditioner, a control method thereon, a controller, and a storage medium. Background Technology

[0002] Currently, for heat pump and air conditioning systems, the outdoor unit functions as a condenser and evaporator in cooling and heating modes, respectively. During condensation, the condensed liquid forms a liquid film on the pipe wall, creating thermal resistance and flow resistance in the condensation heat transfer process. During evaporation, excessive vaporized refrigerant leads to deterioration of evaporative heat transfer and increases evaporator flow resistance. Therefore, existing heat exchangers significantly limit the performance of air conditioners. Furthermore, the optimal number of flow paths for the heat exchanger varies depending on the cooling and heating modes, as well as different frequencies, but existing heat exchangers typically cannot adjust the number of flow paths according to actual operating conditions.

[0003] In related technologies, liquid-liquid separation condensation and gas bypass evaporation technologies are used to improve the performance degradation of heat exchangers caused by excessive condensation and evaporation. However, because the inlet and outlet pipes of the gas-liquid separators in liquid-liquid separation condensation and gas bypass evaporation technologies are different, these two technologies can currently only be used individually and cannot be integrated into the same outdoor or indoor unit. Furthermore, existing heat exchangers using phase separation technology are highly specific and cannot change the number of flow paths in both cooling and heating modes. In addition, when the heat exchanger operates under different loads, without controlling the flow rates of the gaseous and liquid refrigerants, insufficient superheat at the evaporator outlet or insufficient subcooling at the condenser outlet can easily occur, affecting heat exchanger performance. Summary of the Invention

[0004] This application aims to at least solve one of the technical problems existing in the prior art. To this end, this application proposes a heat exchanger, an air conditioner, a control method thereof, a controller, and a storage medium, which can improve the phenomenon of heat exchanger performance degradation caused by excessive condensate and evaporation gas, and can also realize the change of the number of flow paths under different heat exchange modes. In addition, it can ensure that the heat exchanger operates in a highly efficient and stable state, thereby improving the performance of the air conditioner.

[0005] In a first aspect, embodiments of the present invention provide a heat exchanger, comprising: First heat exchange assembly, second heat exchange assembly, and third heat exchange assembly; A gas-liquid separator includes an inlet, a gas phase outlet, and a liquid phase outlet, wherein the gas phase outlet is connected to a second heat exchange component via a first throttling device, and the liquid phase outlet is connected to the second heat exchange component. The first four-way valve, wherein the first valve port, the second valve port, the third valve port and the fourth valve port of the first four-way valve are respectively connected to the first heat exchange component, the third heat exchange component, the input port and the second heat exchange component; A one-way valve, the inlet of which is connected to the second heat exchange assembly, and the outlet of which is connected to the first heat exchange assembly.

[0006] According to some embodiments of this application, the first four-way valve is also connected to the compressor's exhaust port or a high-pressure pipeline connected to the exhaust port via a first connecting pipe, and to the compressor's suction port or a low-pressure pipeline connected to the suction port via a second connecting pipe.

[0007] According to some embodiments of this application, at least one of the following is included: The number of flow path branches in the first heat exchange component is greater than the number of flow path branches in the second heat exchange component; The number of flow path branches in the second heat exchange component is greater than the number of flow path branches in the third heat exchange component.

[0008] According to some embodiments of this application, including: The number of U-tubes in the second heat exchange component and the third heat exchange component is 0.2 to 0.55 times the number of U-tubes in the first heat exchange component; the number of U-tubes in the third heat exchange component is 0.05 to 0.3 times the number of U-tubes in the first heat exchange component and the second heat exchange component.

[0009] According to some embodiments of this application, the first throttling device is one of the following: an electronic expansion valve, or a capillary tube.

[0010] In a second aspect, embodiments of the present invention provide an air conditioner including a heat exchanger as described in the first aspect above.

[0011] Thirdly, embodiments of the present invention provide a control method for an air conditioner, applied to the air conditioner described in the second aspect above. The heat exchanger in the air conditioner includes a first throttling device and a first four-way valve. The first four-way valve includes a first valve port, a second valve port, a third valve port, and a fourth valve port. The first throttling device is a first expansion valve. The method includes: Obtain the heat exchange mode of the air conditioner; According to the heat exchange mode, the conduction state of the first four-way valve and the opening degree of the first expansion valve are controlled.

[0012] According to some embodiments of this application, the heat exchange mode includes a heating mode, and controlling the conduction state of the first four-way valve and the opening degree of the first expansion valve according to the heat exchange mode includes: When the air conditioner is running in heating mode, the passage from the first valve port to the fourth valve port and the passage from the second valve port to the third valve port in the first four-way valve are opened. Obtain the target operating frequency of the compressor, and determine the initial opening degree of the first expansion valve based on the target operating frequency; The evaporation superheat of the heat exchanger is obtained at a first preset time interval, and the target opening degree of the first expansion valve is obtained based on the evaporation superheat; wherein, the evaporation superheat is obtained by subtracting the second temperature value at the compressor suction port from the first temperature value at the heat exchanger.

[0013] According to some embodiments of this application, obtaining the target opening degree of the first expansion valve based on the evaporation superheat includes: The evaporation superheat is compared with at least one preset temperature value, and the opening adjustment value is determined based on the comparison result. The target opening of the first expansion valve is obtained by adding the initial opening to the opening adjustment value.

[0014] According to some embodiments of this application, the heat exchange mode further includes a cooling mode, and controlling the conduction state of the first four-way valve and the opening degree of the first expansion valve according to the heat exchange mode includes: When the air conditioner is running in cooling mode, the passage from the first valve port to the third valve port and the passage from the fourth valve port to the second valve port in the first four-way valve are opened. Adjust the opening of the first expansion valve to its maximum.

[0015] Fourthly, embodiments of the present invention provide a controller, including a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the program to implement the control method for an air conditioner as described in the third aspect above.

[0016] Fifthly, embodiments of the present invention provide a computer-readable storage medium storing computer-executable instructions for causing a computer to perform the control method for an air conditioner as described in the third aspect above.

[0017] According to the technical solution of the embodiments of this application, at least the following beneficial effects are achieved: In the cooling mode, due to the one-way conduction of the one-way valve, the refrigerant flows into the first heat exchange component, and after being condensed once by the first heat exchange component, it flows to the gas-liquid separator after passing through the first four-way valve. The gaseous refrigerant separated by the gas-liquid separator passes through the first throttling device and flows to the second heat exchange component for secondary condensation. The liquid refrigerant separated by the gas-liquid separator merges with the refrigerant after secondary condensation and flows to the third heat exchange component for tertiary condensation. In the heating mode, after the refrigerant evaporates once by the third heat exchange component, it flows to the gas-liquid separator after passing through the first four-way valve. The liquid refrigerant separated by the gas-liquid separator flows to the second heat exchange component and the first heat exchange component for secondary evaporation, respectively. The gaseous refrigerant separated by the gas-liquid separator merges with the refrigerant after secondary evaporation after passing through the first throttling device. First, this application embodiment designs a phase-separation heat exchanger that can apply liquid-liquid separation condensation technology and gas bypass evaporation technology in cooling and heating modes respectively. The refrigerant flow direction at the inlet and outlet of the gas-liquid separator does not change due to switching between cooling and heating modes, effectively ensuring its gas-liquid separation efficiency. Second, this application embodiment can use a gas-liquid separator to separate the condensate in cooling mode, effectively improving the condensation heat transfer coefficient. Furthermore, it can apply gas bypass evaporation technology in heating mode, effectively reducing the area of ​​the mist flow region, thereby increasing the effective heat exchange area of ​​the heat exchanger and reducing refrigerant-side resistance loss. Moreover, the heat exchanger designed in this application embodiment can change the number of flow paths in evaporation / condensation modes. When changing the flow paths, several flow paths can be significantly increased or decreased, with various variation methods. In addition, this application embodiment can control the gas phase outlet flow rate of the gas-liquid separator through a first throttling device in different heat exchange modes to ensure that the heat exchanger is in a highly efficient and stable operating state. Therefore, the embodiments of this application can improve the phenomenon of heat exchanger performance degradation caused by excessive condensate and evaporated gas, and can also realize the change of the number of flow paths under different heat exchange modes. In addition, the gas phase outlet flow rate can be controlled under different heat exchange modes to ensure that the heat exchanger operates in a highly efficient and stable state.

[0018] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0019] The accompanying drawings are used to provide a further understanding of the technical solutions of this application and constitute a part of the specification. They are used together with the embodiments of this application to explain the technical solutions of this application and do not constitute a limitation on the technical solutions of this application.

[0020] Figure 1 This is a schematic diagram of a system architecture platform for performing a control method for an air conditioner according to an embodiment of this application; Figure 2 This is a schematic diagram of the structure of a heat exchanger provided in one embodiment of this application; Figure 3 This is a schematic diagram of the state of the first four-way valve in heating mode provided in one embodiment of this application; Figure 4 This is a schematic diagram of the state of the first four-way valve in the cooling mode provided in one embodiment of this application; Figure 5 This is a schematic diagram of a heat exchanger with a capillary tube as the throttling device provided in one embodiment of this application; Figure 6 This is a schematic diagram of the structure of a heat exchanger with a different number of flow path branches according to one embodiment of this application; Figure 7 This is a schematic diagram of the refrigerant flow direction in the cooling mode of an air conditioner provided in one embodiment of this application; Figure 8 This is a schematic diagram of the refrigerant flow direction in heating mode of an air conditioner provided in one embodiment of this application; Figure 9 This is a flowchart of an air conditioner control method provided in one embodiment of this application; Figure 10 This is a flowchart of a control method for an air conditioner provided in another embodiment of this application; Figure 11 This is a flowchart of a control method for an air conditioner provided in another embodiment of this application; Figure 12 This is a flowchart of a control method for an air conditioner provided in another embodiment of this application. Detailed Implementation

[0021] The embodiments of this application are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this application, and should not be construed as limiting this application.

[0022] In the description of this application, it should be understood that the orientation descriptions, such as up, down, front, back, left, right, etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.

[0023] In the description of this application, "several" means one or more, "more than" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. The use of "first" and "second" in the description is merely for distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0024] In the description of this application, unless otherwise expressly defined, terms such as "setup," "installation," and "connection" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this application in conjunction with the specific content of the technical solution.

[0025] This application provides a heat exchanger, an air conditioner, a control method, a controller, and a storage medium, which can improve the phenomenon of heat exchanger performance degradation caused by excessive condensate and evaporation gas. It can also change the number of flow paths under different heat exchange modes, and control the gas phase outlet flow rate under different heat exchange modes to ensure that the heat exchanger operates in a highly efficient and stable state, thereby improving the performance of the air conditioner.

[0026] The embodiments of this application will be further described below with reference to the accompanying drawings.

[0027] like Figure 1 As shown, Figure 1 This is a schematic diagram of a system architecture platform for performing a control method for an air conditioner, provided in one embodiment of this application.

[0028] The system architecture platform 100 of this application embodiment includes one or more processors 110 and memory 120. Figure 1 The example uses a processor 110 and a memory 120.

[0029] Processor 110 and memory 120 can be connected via a bus or other means. Figure 1 Taking the example of a connection between China and Israel via a bus.

[0030] Memory 120, as a non-transitory computer-readable storage medium, can be used to store non-transitory software programs and non-transitory computer-executable programs. Furthermore, memory 120 may include high-speed random access memory, and may also include non-transitory memory, such as at least one disk storage device, flash memory device, or other non-transitory solid-state storage device. In some embodiments, memory 120 may optionally include memory 120 remotely located relative to processor 110, and these remote memories can be connected to the system architecture platform 100 via a network. Examples of such networks include, but are not limited to, the Internet, corporate intranets, local area networks, mobile communication networks, and combinations thereof.

[0031] Those skilled in the art will understand that Figure 1 The device structure shown does not constitute a limitation on the system architecture platform 100, and may include more or fewer components than shown, or combine certain components, or have different component arrangements.

[0032] exist Figure 1 In the system architecture platform 100 shown, the processor 110 can be used to call the control program of the air conditioner stored in the memory 120, thereby realizing the control method of the air conditioner.

[0033] Based on the hardware structure of the above-mentioned system architecture platform 100, various embodiments of the heat exchanger and air conditioner of this application are proposed.

[0034] Firstly, such as Figure 2 As shown, this embodiment of the invention provides a heat exchanger, including: a first heat exchange component 200, a second heat exchange component 300, a third heat exchange component 400, a gas-liquid separator 500, a first throttling device 600, a first four-way valve 700, and a one-way valve DF1; wherein, the gas-liquid separator 500 includes an inlet, a gas phase outlet 510, and a liquid phase outlet 520, wherein the gas phase outlet 510 is connected to the second heat exchange component 300 through the first throttling device 600, and the liquid phase outlet 520 is connected to the second heat exchange component 300; the first valve port A, the second valve port B, the third valve port C, and the fourth valve port D of the first four-way valve 700 are respectively connected to the first heat exchange component 200, the third heat exchange component 400, the inlet, and the second heat exchange component 300; the inlet of the one-way valve DF1 is connected to the second heat exchange component 300, and the outlet of the one-way valve DF1 is connected to the first heat exchange component 200.

[0035] Specifically, refer to Figure 2 and Figure 7 In cooling mode, due to the one-way conduction of the one-way valve DF1, the refrigerant flows into the first heat exchange component 200. After being condensed once by the first heat exchange component 200, it flows to the gas-liquid separator 500 after passing through the first four-way valve 700. The gaseous refrigerant separated by the gas-liquid separator 500 flows to the second heat exchange component 300 for secondary condensation after passing through the first throttling device 600. The liquid refrigerant separated by the gas-liquid separator 500 merges with the refrigerant after secondary condensation and flows to the third heat exchange component 400 for tertiary condensation.

[0036] Additionally, refer to Figure 2 and Figure 8In heating mode, after the refrigerant evaporates once through the third heat exchange component 400, it flows to the gas-liquid separator 500 through the first four-way valve 700. The liquid refrigerant separated by the gas-liquid separator 500 flows to the second heat exchange component 300 and the first heat exchange component 200 for secondary evaporation. The gaseous refrigerant separated by the gas-liquid separator 500 merges with the refrigerant after secondary evaporation after passing through the first throttling device 600.

[0037] It is worth noting that, firstly, the embodiments of this application design a phase separation heat exchanger, which can apply liquid-liquid separation condensation technology and gas bypass evaporation technology in cooling and heating modes respectively. Furthermore, the refrigerant flow direction at the inlet and outlet of the gas-liquid separator does not change due to switching between cooling and heating modes, effectively ensuring its gas-liquid separation efficiency. Secondly, the embodiments of this application can use a gas-liquid separator to separate the condensate in cooling mode, effectively improving the condensation heat transfer coefficient. Moreover, in heating mode, gas bypass evaporation technology can be applied to effectively reduce the area of ​​the mist flow region, thereby increasing the effective heat exchange area of ​​the heat exchanger and reducing refrigerant-side resistance loss. Furthermore, the heat exchanger designed in the embodiments of this application can achieve changes in the number of flow paths during evaporation / condensation modes. When changing the flow paths, several flow paths can be significantly increased or decreased, with various variation methods. In addition, the embodiments of this application can also control the gas phase outlet flow rate of the gas-liquid separator through a first throttling device in different heat exchange modes to ensure that the heat exchanger is in a highly efficient and stable operating state. Therefore, the embodiments of this application can improve the phenomenon of heat exchanger performance degradation caused by excessive condensate and evaporated gas, and can also realize the change of the number of flow paths under different heat exchange modes. In addition, the gas phase outlet flow rate can be controlled under different heat exchange modes to ensure that the heat exchanger operates in a highly efficient and stable state.

[0038] like Figure 3 and Figure 4 As shown, in some embodiments, the first four-way valve 700 further includes: a valve body 710; a valve core 720, including a connecting isolator 721, wherein the valve core 720 is disposed in the valve body 710 to divide the valve body 710 into a first chamber 711, a second chamber 712 and a third chamber 713, wherein the connecting isolator 721, the first valve port A, the second valve port B, the third valve port C and the fourth valve port D are all disposed in the second chamber 712; the connecting isolator 721 is used to move left and right under the action of the pressure difference between the first chamber 711 and the third chamber 713 to determine the passage of the first four-way valve 700.

[0039] In some embodiments, combined with Figure 3 , Figure 4 and Figure 7The first four-way valve 700 further includes: a pilot valve 730, a first connecting pipe 740, a second connecting pipe 750, a third connecting pipe 760, and a fourth connecting pipe 770; wherein, the pilot valve 730 is connected to the exhaust port 911 of the compressor 910 through the first connecting pipe 740 and to the intake port 912 of the compressor 910 through the second connecting pipe 750; the third connecting pipe 760 is connected between the valve body 710 and the pilot valve 730, connecting the first chamber 711 and the pilot valve 730; the fourth connecting pipe 770 is connected between the valve body 710 and the pilot valve 730, connecting the third chamber 713 and the pilot valve 730.

[0040] Understandably, one end of the first connecting pipe 740 is connected to the pilot valve 730, and the other end is connected to the exhaust port 911 on the high-pressure side of the compressor; one end of the second connecting pipe 750 is connected to the pilot valve 730, and the other end is connected to the intake port 912 on the low-pressure side of the compressor.

[0041] Specifically, the fourth valve port D, the second valve port B, and the third valve port C are arranged side by side in sequence. The valve core 720 includes two pistons and a connecting member between the two pistons. The two pistons are spaced apart from each other, dividing the interior of the valve body 710 into a first chamber 711, a second chamber 712, and a third chamber 713. A communicating isolation member 721 is provided on the connecting member. The communicating isolation member 721 protrudes in a direction away from the second valve port B and towards the fourth valve port D.

[0042] Combination Figure 4 In cooling mode, when the first four-way valve 700 is not energized, the pilot valve 730 connects the first connecting pipe 740 to the fourth connecting pipe 770 and the second connecting pipe 750 to the third connecting pipe 760. This connects the first chamber 711 to the low-pressure side of the compressor and the third chamber 713 to the high-pressure side of the compressor. The pressure in the third chamber 713 is greater than the pressure in the first chamber 711. Under the action of the pressure difference, the valve core 720 moves to the left, and the connecting isolator 721 moves above the fourth valve port D and the second valve port B, thus opening the passage from the fourth valve port D to the second valve port B and the passage from the first valve port A to the third valve port C.

[0043] In addition, combined Figure 3In heating mode, when the first four-way valve 700 is energized, the pilot valve 730 is switched to connect the first connecting pipe 740 with the third connecting pipe 760 and the second connecting pipe 750 with the fourth connecting pipe 770. This connects the first chamber 711 to the high-pressure side of the compressor and the third chamber 713 to the low-pressure side of the compressor. The pressure in the first chamber 711 is greater than the pressure in the third chamber 713. Under the action of the pressure difference, the valve core 720 moves to the right, and the connecting isolator 721 moves above the second valve port B and the third valve port C, so that the passage from the fourth valve port D to the first valve port A and the passage to the third valve port C are open.

[0044] Understandably, traditional four-way valves connect a connecting pipe between the valve body and the valve port, using the pressure of the refrigerant flowing into the valve to drive the valve to switch its passage. However, when using a traditional four-way valve, there may be insufficient refrigerant pressure, making it difficult to switch the valve's passage. In this embodiment, a pilot valve 730 is provided, connected to a first connecting pipe 740 at the compressor discharge port, and a second connecting pipe 750, a third connecting pipe 760, and a fourth connecting pipe 770 at the compressor suction port. This utilizes the pressure difference between the high-pressure and low-pressure sides of the compressor to switch the passage of the first four-way valve 700, ensuring a smooth switching process for the first four-way valve 700.

[0045] In some embodiments, the number of flow path branches in the first heat exchange component 200 is greater than the number of flow path branches in the second heat exchange component 300; the number of flow path branches in the second heat exchange component 300 is greater than the number of flow path branches in the third heat exchange component 400. The first heat exchange component 200 and the second heat exchange component 300 are modular variable flow path components.

[0046] In one embodiment, simulation and experimental data show that the number of U-tubes in the second heat exchange component 300 and the third heat exchange component 400 is 0.2 to 0.55 times the number of U-tubes in the first heat exchange component 200; for example, in an embodiment of this application, the number of U-tubes in the second heat exchange component 300 and the third heat exchange component 400 can be 0.5 times the number of U-tubes in the first heat exchange component 200.

[0047] In another embodiment, simulation and experimental data show that the number of U-tubes in the third heat exchange component 400 is 0.05 to 0.3 times the number of U-tubes in the first heat exchange component 200 and the second heat exchange component 300; for example, in the embodiments of this application, the number of U-tubes in the third heat exchange component 400 can be 0.1 times the number of U-tubes in the first heat exchange component 200 and the second heat exchange component 300.

[0048] In some embodiments, the first throttling device 600 is one of the following: an electronic expansion valve, a capillary tube. Specifically, Figure 2As shown, the first throttling device 600 is an electronic expansion valve. The gas phase outlet flow rate of the gas-liquid separator 500 can be controlled by controlling the opening degree of the electronic expansion valve.

[0049] Furthermore, in some embodiments, such as Figure 5 and Figure 6 As shown, the heat exchanger also includes a first throttling device 600 and a second throttling device 800. The first throttling device 600 is located at the gas phase outlet 510 of the gas-liquid separator 500, and the second throttling device 800 is located at the liquid phase outlet 520 of the gas-liquid separator 500.

[0050] In one embodiment, such as Figure 5 As shown, the first throttling device 600 and the second throttling device 800 can be capillary tubes. It should be noted that under single load conditions, an electronic expansion valve is not required in the flow path of the heat exchanger; using a capillary tube instead of an electronic expansion valve can save costs.

[0051] In one embodiment, such as Figure 6 As shown, the first throttling device 600 and the second throttling device 800 can be electronic expansion valves; the gas phase outlet flow rate of the gas-liquid separator 500 can be controlled by controlling the opening degree of the first throttling device 600; and the liquid phase outlet flow rate of the gas-liquid separator 500 can be controlled by controlling the opening degree of the second throttling device 800. It is understandable that after the flow path in the heat exchanger becomes more complex, the throttling effect of a single tube is not good, and the throttling effect can be enhanced by adding the second throttling device 800.

[0052] Understandably, the capillary tube mentioned above is the simplest throttling device in an air conditioner. It is a copper tube of a specified length, with an inner diameter typically ranging from 0.5 mm to 2 mm. Its advantages are ease of manufacture and low cost; its disadvantage is the lack of flow regulation functionality.

[0053] Furthermore, it is understandable that the aforementioned electronic expansion valve can be structured into three parts: detection, control, and execution. Its advantages include a wide flow adjustment range, high control precision, suitability for intelligent control, and the ability to adapt to rapid changes in refrigerant flow for high efficiency. The electronic expansion valve can be considered a smart capillary tube with a variable inner diameter.

[0054] Based on the above-described hardware structure of the heat exchanger, the heat exchanger provided in the first aspect embodiment of this application will be further described.

[0055] In some embodiments, refer to Figure 2 and Figure 6The first heat exchange component 200 and the second heat exchange component 300 are modular variable flow path components. The second heat exchange component 300 is connected to the inlet of the one-way valve DF1, and the first heat exchange component 200 is connected to the outlet of the one-way valve DF1. The direction from the inlet to the outlet of the one-way valve DF1 is the conduction direction of the one-way valve DF1. Because the one-way valve DF1 has a unidirectional conduction property, the first one-way valve DF1 can be used to implement the variable flow path module.

[0056] Understandably, in combination Figure 7 In cooling mode, the refrigerant flows entirely into the first heat exchange component 200 and does not flow into the second heat exchange component 300. When the number of flow path branches in the first heat exchange component 200 is N, the refrigerant is divided into N paths to achieve one condensation in the first heat exchange component 200. After one condensation, the refrigerant flows into the gas-liquid separator 500 through the first four-way valve 700. The gaseous refrigerant separated by the gas-liquid separator 500 flows to the second heat exchange component 300 after passing through the first throttling device 600. When the number of flow path branches in the second heat exchange component 300 is M, the gaseous refrigerant is divided into M paths to undergo a second condensation in the second heat exchange component 300. The liquid refrigerant separated by the gas-liquid separator merges with the refrigerant after the second condensation and flows into the third heat exchange component 400. When the number of flow path branches in the third heat exchange component 400 is R, the refrigerant is divided into R paths to undergo a third condensation in the third heat exchange component 400. In cooling mode, the refrigerant flows through three tube passes: N paths in the first pass, M paths in the second pass, and R paths in the third pass. (Combined with...) Figure 8 In heating mode, the refrigerant is divided into R paths and undergoes primary evaporation in the third heat exchange component 400. After passing through the first four-way valve 700, it flows to the gas-liquid separator 500. The liquid refrigerant separated by the gas-liquid separator 500 flows to the second heat exchange component 300 and the first heat exchange component 200, respectively. The liquid refrigerant is then divided into (M+N) paths for secondary evaporation in the first and second heat exchange components 200 and 300. The gaseous refrigerant separated by the gas-liquid separator 500 passes through the first throttling device 600 and merges with the refrigerant after secondary evaporation. In other words, in heating mode, the refrigerant flows through two tube passes: the first tube pass has R paths, and the second tube pass has (M+N) paths.

[0057] Therefore, the variable flow path module in the heat exchanger of this application embodiment can realize the change of the number of flow paths in evaporation / condensation mode. That is, the number of flow path branches N+M of the variable flow path module in condensation mode can be changed to the number of flow path branches (N+M) of the variable flow path module in evaporation mode.

[0058] It should be noted that for heat exchangers of different areas or capacities, the number of flow path branches can be varied between R+(N+M) and R+N+M by combining variable flow path modules with commonly used subcooling section flow paths. This allows the heat exchanger to function as a condenser, where the pressure loss is relatively small, requiring fewer flow path branches to increase the refrigerant flow rate and thus the heat transfer coefficient. Conversely, when the heat exchanger functions as an evaporator, the decrease in the logarithmic mean temperature difference caused by the pressure loss has a dominant impact on the heat transfer, requiring more flow path branches to increase the heat transfer.

[0059] Understandably, the number of flow path branches N in the first heat exchange component 200, the number of flow path branches M in the second heat exchange component 300, and the number of flow path branches R in the third heat exchange component 400 can be set according to the actual heat exchange requirements.

[0060] For example, regarding the variable flow path module and phase separation heat exchanger configuration, refer to... Figure 2 As shown, the heat exchanger serves as a condenser and is divided into three parts: the upper, middle, and lower heat exchangers have 50%, 33%, and 17% flow paths, respectively. The upper and middle heat exchangers are modular variable flow path sections with N / M flow paths. To ensure the refrigerant flow rate during liquid separation and condensation, N > M under normal circumstances. The lower heat exchanger can serve as a subcooling section in the condenser.

[0061] For example, such as Figure 6 As shown, in the heat exchanger, the number of flow path branches N in the first heat exchange component 200 is 6, the number of flow path branches M in the second heat exchange component 300 is 4, and the number of flow path branches R in the third heat exchange component 400 is 2. Therefore, in condensation mode, the three tube passes have 6+4+2 paths, and in evaporation mode, the two tube passes have (6+4)+2 paths, achieving changes in the number of flow path branches of N+M+R and (N+M)+R in the heat exchanger.

[0062] In one embodiment, Figure 2 The heat exchanger used is a double-row heat exchanger. Alternatively, the heat exchanger can also be a single-row or triple-row heat exchanger.

[0063] In one embodiment, the present application designs a phase separation heat exchanger that can apply liquid-liquid condensation technology and gas bypass evaporation technology in cooling and heating modes respectively. The refrigerant flow direction at the inlet and outlet of the gas-liquid separator will not change due to the switching between cooling and heating modes. Therefore, more efficient and compact gas-liquid separators, such as cyclone separators and filter separators, can be used, rather than being limited to traditional gravity gas-liquid separators, effectively ensuring its gas-liquid separation efficiency.

[0064] Those skilled in the art will understand that the structure described above does not constitute a limitation on the heat exchanger, and may include more or fewer components than illustrated, or combine certain components, or have different component arrangements.

[0065] Based on the above-mentioned system architecture platform 100 and the hardware structure of the heat exchanger, an overall embodiment of the air conditioner of this application is proposed.

[0066] like Figure 7 and Figure 8 As shown, in a second aspect, embodiments of this application provide an air conditioner 900, including: a compressor 910, a second four-way valve 920, an indoor unit 930, a third expansion valve EEV3, and as shown in the figure. Figure 2 The heat exchanger shown.

[0067] The compressor 910 includes an exhaust port 911 and an intake port 912. The four ports of the second four-way valve 920 are respectively connected to the exhaust port 911, the intake port 912, the first heat exchange component 200 in the heat exchanger, and one end of the indoor unit 930. The other end of the indoor unit 930 is connected to the third heat exchange component 400 in the heat exchanger. Furthermore, according to some embodiments of this application, the first four-way valve 700 is also connected via a first connecting pipe 740 to the exhaust port 911 of the compressor 910 or a high-pressure pipeline connected to the exhaust port 911, and via a second connecting pipe 750 to the intake port 912 of the compressor 910 or a low-pressure pipeline connected to the intake port 912. It should be noted that the high-pressure pipeline can refer to the pipeline connected between the exhaust port 911 and the second four-way valve 920, and the low-pressure pipeline can refer to the pipeline connected between the intake port 912 and the second four-way valve 920.

[0068] According to the air conditioner provided in the second aspect embodiment of this application, the first throttling device 600 in the heat exchanger is a first expansion valve EEV1. For example... Figure 7As shown, when the air conditioner is operating in cooling mode, high-temperature and high-pressure refrigerant is discharged from the compressor exhaust port 911 and enters the upper gas collection pipe from the left side of the diagram. Since the first one-way valve DF1 is not open at this time, the refrigerant only flows through the upper first heat exchange component 200. The refrigerant is divided into three paths and undergoes one condensation in the first heat exchange component 200. After the three refrigerant paths merge, they flow from the first valve port A of the first four-way valve 700 to the third valve port C, and then flow into the gas-liquid separator 500. The gaseous refrigerant obtained after separation by the gas-liquid separator 500 flows out from the gas phase outlet, passes through the first expansion valve EEV1, and then enters the gas phase. The refrigerant enters the lower gas collection pipe and then splits into two paths to enter the second heat exchange component 300 for secondary condensation. The liquid refrigerant separated by the gas-liquid separator 500 merges with the refrigerant after secondary condensation. After merging, the refrigerant is either a pure liquid phase or a gas-liquid two-phase flow. It flows from the fourth valve port D of the first four-way valve 700 to the second valve port B and flows into the third heat exchange component 400 for tertiary condensation and subcooling. After tertiary condensation, the refrigerant passes through the third expansion valve EVV3 for throttling and then enters the indoor unit 930 (evaporator) for evaporation. Finally, it returns to the compressor 910 through the second four-way valve 920 and the suction port 912.

[0069] like Figure 8 As shown, when the air conditioner is operating in heating mode, the outdoor unit is in evaporator mode. The high-temperature, high-pressure refrigerant, after being compressed by the compressor, enters the indoor unit 930 and condenses into a high-pressure liquid state. After being throttled by the third expansion valve EVV3, the refrigerant enters the third heat exchange assembly 400 from the bottom right for partial evaporation. Then, the refrigerant enters the gas-liquid separator 500 through the BC passage of the first four-way valve 700. The gaseous refrigerant after gas-liquid separation enters the flute tube after passing through the first expansion valve EEV1, achieving gas bypass evaporation to reduce evaporator pressure drop and improve heat exchanger performance. The liquid refrigerant after gas-liquid separation is divided into two paths. One path enters the second heat exchange assembly 300 for evaporation in two separate paths. The other path enters the first heat exchange assembly 200 through the DA passage of the first four-way valve 700, and then splits into three paths (paths 1, 2, and 3) for evaporation. After evaporation, it merges with the gaseous refrigerant passing through the first one-way valve DF1, and finally returns to the compressor 910 through the second four-way valve 920 and the suction port 912.

[0070] Therefore, in cooling mode, the outdoor unit acts as a condenser, and the condensed liquid forms a liquid film on the condenser wall. This liquid film separates the gaseous refrigerant from the wall, becoming the thermal resistance in the condensation heat transfer process. Furthermore, the liquid film gradually thickens as the condensation process progresses, leading to a gradual increase in thermal resistance and significantly affecting condenser performance. Using a gas-liquid separator to separate the condensate can effectively improve the condensation heat transfer coefficient. In addition, by reducing the number of branch lines in the tube after gas-liquid separation, the average flow velocity inside the tube can be maintained, further enhancing the condensation heat transfer process. In heating mode, the outdoor unit acts as the evaporator. During the evaporation process, the refrigerant flow pattern increases with its dryness, successively becoming single-liquid flow, bubbly flow, slug flow, annular flow, mist flow, and single-gas flow. In the mist flow region, due to the excessive dryness of the refrigerant, the liquid film on the inner surface of the pipe is destroyed, leading to deteriorated heat transfer and a sharp decrease in the heat transfer coefficient. This significantly affects the heat exchange performance of the evaporator. Applying gas bypass evaporation technology can effectively reduce the area of ​​the mist flow region, thereby increasing the effective heat exchange area of ​​the heat exchanger and reducing refrigerant-side resistance loss, thus improving the overall performance of the evaporator. In other words, the air conditioner provided in this application can improve the phenomenon of heat exchanger performance degradation caused by excessive condensate and evaporated gas. It can also change the number of flow paths in different heat exchange modes and control the gas phase outlet flow rate in different heat exchange modes to ensure that the heat exchanger operates in a highly efficient and stable state, thereby improving the performance of the air conditioner.

[0071] Those skilled in the art will understand that the structure described above does not constitute a limitation on the air conditioner, and may include more or fewer components than illustrated, or combine certain components, or have different component arrangements.

[0072] Based on the above-mentioned system architecture platform 100 and the hardware structure of the air conditioner, various embodiments of the air conditioner control method of this application are proposed.

[0073] Thirdly, such as Figure 9 As shown, Figure 9 This is a flowchart of a control method for an air conditioner provided in one embodiment of this application. The control method can be applied to an air conditioner provided in a second aspect embodiment, wherein the first throttling device in the air conditioner is a first expansion valve, and the control method for the air conditioner may include, but is not limited to, steps S100 and S200.

[0074] Step S100: Obtain the heat exchange mode of the air conditioner; Step S200: According to the heat exchange mode, control the conduction state of the first four-way valve and the opening degree of the first expansion valve.

[0075] In this embodiment, through steps S100 and S200, after the air conditioner is started, the heat exchange mode of the air conditioner is detected and acquired. Then, according to the heat exchange mode, the conduction state of the first four-way valve and the opening degree of the first expansion valve are controlled. In different heat exchange modes, the refrigerant flow direction is different. The first four-way valve can be used to switch between liquid-liquid condensation technology and phase separation technology in cooling and heating modes, and to switch the connection between the high and low pressure capillary tubes and the exhaust and intake ports, ensuring smooth switching of the first four-way valve's path. When operating in different modes, the opening degree of the first expansion valve is controlled to adjust the gas phase outlet flow rate of the gas-liquid separator in cooling and heating modes, ensuring that the heat exchanger operates in a highly efficient and stable state, thereby improving the performance of the air conditioner. In other words, the air conditioner control method provided in this embodiment can improve the phenomenon of heat exchanger performance degradation caused by excessive condensate and evaporation gas, and can also change the number of flow paths in different heat exchange modes. Furthermore, it can control the gas phase outlet flow rate in different heat exchange modes to ensure that the heat exchanger operates in a highly efficient and stable state, thereby improving the performance of the air conditioner.

[0076] It is understood that the type of heat exchange mode mentioned above can be a cooling mode, a heating mode, or a dehumidification mode. This application embodiment does not specifically limit the type of heat exchange mode.

[0077] like Figure 10 As shown, step S200 may include, but is not limited to, steps S310, S320 and S330.

[0078] Step S310: When the air conditioner is running in heating mode, control the passage from the first valve port to the fourth valve port and the passage from the second valve port to the third valve port in the first four-way valve to be opened. Step S320: Obtain the target operating frequency of the compressor, and determine the initial opening degree of the first expansion valve based on the target operating frequency; Step S330: Obtain the evaporation superheat of the heat exchanger at a first preset time interval, and obtain the target opening degree of the first expansion valve based on the evaporation superheat; wherein, the evaporation superheat is obtained by subtracting the second temperature value at the compressor suction port from the first temperature value at the heat exchanger.

[0079] Through steps S310 to S330, when the air conditioner is operating in heating mode, firstly, the passages from the first valve port to the fourth valve port and from the second valve port to the third valve port in the first four-way valve are opened; then, the target operating frequency of the compressor is obtained, and the initial opening of the first expansion valve is determined according to the target operating frequency; at this time, when the air conditioner is operating in heating mode, the outdoor unit is in evaporator mode. The high-temperature and high-pressure refrigerant after being compressed by the compressor enters the indoor unit and condenses into a high-pressure liquid state. After being throttled by the third expansion valve EVV3, the refrigerant enters the third heat exchange component 400 from the bottom right for primary evaporation. The refrigerant after primary evaporation enters the gas-liquid separator through the passage from the second valve port B to the third valve port C of the first four-way valve. The gaseous refrigerant after gas-liquid separation enters the flute tube after passing through the first expansion valve EEV1, realizing gas bypass evaporation to reduce the evaporator pressure drop and improve the heat exchanger performance. After gas-liquid separation, the liquid refrigerant is divided into two paths. One path enters the second heat exchange component 300, while the other path flows into the first heat exchange component 200 via the passage from the fourth port to the first port of the first four-way valve 700. The refrigerant undergoes secondary evaporation in both the second and first heat exchange components 300. The gaseous refrigerants from the secondary evaporation then merge and finally return to the compressor 910 via the second four-way valve 920 and the suction port 912. Furthermore, during this heating process, the evaporation superheat can be obtained by subtracting the second temperature at the compressor suction port from the first temperature at the heat exchanger. This evaporation superheat is acquired at first preset intervals, and the target opening of the first expansion valve is determined based on this superheat. Under different operating load conditions, where the mass ratio of the gas and liquid phases entering the gas-liquid separator varies, the gas bypass evaporator can be kept at different openings to ensure optimal operation of the gas bypass evaporator.

[0080] For example, to further illustrate step S320, the initial opening of the first expansion valve is determined based on the target operating frequency. In heating mode, the initial opening of the first expansion valve is set as follows: i) If the target operating frequency Fr≤a, the initial opening degree is the first preset opening degree value A, and it is maintained for the second preset time t1; where a=b*(Fmax+Fmin), the recommended value of b is 0.5, and the value range is 0.45~0.75; Fmax is the maximum operating frequency of the compressor in heating in this system, and Fmin is the minimum operating frequency of the compressor in heating in this system; the recommended value of A is 50P, and the value range is 20P~100P; the recommended time of t1 is 5min, and the value range is 2min~15min.

[0081] ii) If the target operating frequency Fr > a, the initial opening is the second preset opening value B, and it is maintained for the third preset time t2; the recommended value of B is 80P, and the value range is 50P~150P; the recommended time of t2 is 2min, and the value range is 1min~15min.

[0082] It is understandable that a first temperature sensor T3 can be installed in the middle of the second heat exchange component of the heat exchanger, or a second temperature sensor T3B can be installed at the outlet of the third heat exchange component. The first temperature value T3 can be obtained through the first temperature sensor T3 or the second temperature sensor T3B. A third temperature sensor or a low-pressure sensor can be installed at the compressor suction port, and the second temperature value Tx can be obtained through the third temperature sensor or the low-pressure sensor.

[0083] In addition, it is understood that the first preset time, the second preset time and the third preset time mentioned above can be preset, and the embodiments of this application do not specifically limit the duration of the preset time interval.

[0084] like Figure 11 As shown, step S330 may include, but is not limited to, steps S410 and S420.

[0085] Step S410: Compare the evaporation superheat with at least one preset temperature value, and determine the opening adjustment value based on the comparison result; Step S420: Add the initial opening degree to the opening degree adjustment value to obtain the target opening degree of the first expansion valve.

[0086] Through steps S410 and S420, the opening adjustment value can be determined by comparing the evaporation superheat with at least one preset temperature value, and the first expansion valve can be adjusted to maintain different openings to ensure that the gas bypass evaporator operates in the best condition.

[0087] Specifically, the first temperature value T3 and the second temperature value Tx are detected every first preset time tm, and the evaporation superheat is obtained by subtracting the second temperature value Tx from the first temperature value T3. T, specifically, T = T3 - Tx. Based on the degree of evaporative superheat. The opening adjustment value is determined by comparing T with the preset temperature value. The correspondence between the comparison result and the opening adjustment value is shown in Table 1.

[0088] Table 1

[0089] Specifically, at least one preset temperature value includes: -1.5, -0.5, 0.5, and 1.5. The opening adjustment value is determined according to Table 1. After Ec, the target opening of the first expansion valve can be obtained by adding the initial opening degree to the opening degree adjustment value.

[0090] The first preset time tm is recommended to be 40s, ranging from 30s to 300s; m is recommended to be 4P, ranging from 2 to 15P; and n is recommended to be 8P, ranging from 4 to 30P.

[0091] like Figure 12 As shown, the above step S200 may include, but is not limited to, steps S510 and S520.

[0092] Step S510: When the air conditioner is running in cooling mode, control the passage from the first valve port to the third valve port and the passage from the fourth valve port to the second valve port in the first four-way valve to be opened. Step S520: Adjust the opening of the first expansion valve to the maximum.

[0093] Through steps S510 and S520, when the air conditioner is operating in cooling mode, firstly, the passages from the first valve port to the third valve port and from the fourth valve port to the second valve port in the first four-way valve are opened; then, the opening of the first expansion valve is adjusted to the maximum; at this time, in the air conditioner, high-temperature and high-pressure refrigerant is discharged from the compressor discharge port 911. Since the first one-way valve DF1 is not open at this time, the refrigerant flows into the first heat exchange component 200 for primary condensation. The refrigerant after primary condensation flows from the first valve port A to the third valve port C of the first four-way valve 700 and flows into the gas-liquid separator 500. The gas phase obtained after separation by the gas-liquid separator 500... The refrigerant flows out from the gas phase outlet, passes through the first expansion valve EEV1 (whose opening is adjusted to the maximum), and then enters the second heat exchange assembly 300 for secondary condensation. The liquid refrigerant separated by the gas-liquid separator 500 merges with the refrigerant after secondary condensation. After merging, the refrigerant is either a pure liquid phase or a gas-liquid two-phase flow. It flows from the fourth valve port D of the first four-way valve 700 to the second valve port B, and then flows into the third heat exchange assembly 400 for tertiary condensation and subcooling. After tertiary condensation, the refrigerant passes through the third expansion valve EVV3 (throttling) before entering the indoor unit (evaporator) for evaporation, and finally returns to the compressor 910 through the second four-way valve 920 and the suction port 912. In this cooling mode, the average flow rate within the heat exchanger is maintained, effectively improving the condensation heat transfer coefficient.

[0094] In one embodiment, when the air conditioner is heating and defrosting, the first expansion valve in the phase separation heat exchanger is controlled according to the refrigeration principle, and its opening degree is set to 0.

[0095] Based on the heat exchangers, air conditioners, and control methods of the above embodiments, the embodiments of this application also include, but are not limited to, the following technical effects: 1. The module can be used in heat exchangers of various forms, such as tube-fin, or in double-row, single-row, etc.

[0096] 2. Enhanced heat transfer technologies such as variable flow path, liquid separation and condensation, and gas bypass can be implemented in a single heat exchanger. Furthermore, the inlet and outlet of the gas-liquid separator will not be interchanged in different modes, thus allowing the use of more efficient gas-liquid separators, such as cyclone separators and filter separators, rather than being limited to gravity gas-liquid separators.

[0097] 3. When the flow path changes, several flow paths can be increased or decreased significantly. There are many ways to change the flow path, and the flow path conversion between M+N and (M+N) can be realized.

[0098] 4. Under single load conditions, variable flow path technology, gas bypass evaporation and liquid separation condensation technology can be realized without adding control valves, resulting in significant improvement in heat exchanger performance, simple control and low cost.

[0099] Based on the control methods for air conditioners described in the above embodiments, various embodiments of the controller and computer-readable storage medium of this application are presented below.

[0100] Additionally, one embodiment of this application provides a controller comprising: a processor, a memory, and a computer program stored in the memory and executable on the processor.

[0101] The processor and memory can be connected via a bus or other means.

[0102] It should be noted that the controller in this embodiment may include, for example: Figure 1 The processor and memory in the illustrated embodiment belong to the same inventive concept, and therefore have the same implementation principle and beneficial effects, which will not be described in detail here.

[0103] The non-transient software program and instructions required to implement the air conditioner control method of the above embodiments are stored in the memory. When executed by the processor, the air conditioner control method of the above embodiments is executed.

[0104] According to the technical solution of the controller in the embodiments of this application, the phenomenon of heat exchanger performance degradation caused by excessive condensate and evaporation can be improved. It can also change the number of flow paths in different heat exchange modes. In addition, it can control the gas phase outlet flow rate in different heat exchange modes to ensure that the heat exchanger operates in a highly efficient and stable state, thereby improving the performance of the air conditioner.

[0105] It is worth noting that since the controller of this application embodiment can execute the air conditioner control method of any of the above embodiments, the specific implementation method and technical effect of the controller of this application embodiment can refer to the specific implementation method and technical effect of the air conditioner control method of any of the above embodiments.

[0106] Furthermore, one embodiment of this application provides a computer-readable storage medium storing computer-executable instructions for performing the aforementioned air conditioner control method. Exemplarily, the above-described method is executed... Figures 9 to 12 The methods and steps in the text.

[0107] The technical solution of the computer-readable storage medium according to the embodiments of this application can improve the phenomenon of heat exchanger performance degradation caused by excessive condensate and evaporated gas, and can also realize the change of the number of flow paths in different heat exchange modes. In addition, it can control the gas phase outlet flow rate in different heat exchange modes to ensure that the heat exchanger operates in a highly efficient and stable state, thereby improving the performance of the air conditioner.

[0108] It is worth noting that, since the computer-readable storage medium of this application embodiment can execute the air conditioner control method of any of the above embodiments, the specific implementation and technical effects of the computer-readable storage medium of this application embodiment can be referred to the specific implementation and technical effects of the air conditioner control method of any of the above embodiments.

[0109] It will be understood by those skilled in the art that all or some of the steps and systems in the methods disclosed above can be implemented as software, firmware, hardware, and suitable combinations thereof. Some or all of the physical components can be implemented as software executed by a processor, such as a central processing unit, digital signal processor, or microprocessor, or as hardware, or as an integrated circuit, such as an application-specific integrated circuit. Such software can be distributed on a computer-readable medium, which can include computer storage media (or non-transitory media) and communication media (or transient media). As is known to those skilled in the art, the term computer storage media includes volatile and non-volatile, removable and non-removable media implemented in any method or technology for storing information (such as computer-readable instructions, data structures, program modules, or other data). Computer storage media includes, but is not limited to, RAM, ROM, EEPROM, flash memory or other memory technologies, CD-ROM, digital versatile disc (DVD) or other optical disc storage, magnetic cartridges, magnetic tape, disk storage or other magnetic storage devices, or any other medium that can be used to store desired information and is accessible to a computer. Furthermore, as is known to those skilled in the art, communication media typically include computer-readable instructions, data structures, program modules, or other data in modulated data signals such as carrier waves or other transmission mechanisms, and may include any information delivery medium.

[0110] The above provides a detailed description of the preferred embodiments of this application. However, this application is not limited to the above-described embodiments. Those skilled in the art can make various equivalent modifications or substitutions without departing from the spirit of this application. All such equivalent modifications or substitutions are included within the scope defined by the claims of this application.

Claims

1. An air conditioner, characterized in that, Includes a heat exchanger, said heat exchanger comprising: First heat exchange assembly, second heat exchange assembly, and third heat exchange assembly; A gas-liquid separator includes an inlet, a gas phase outlet, and a liquid phase outlet, wherein the gas phase outlet is connected to a second heat exchange component via a first throttling device, and the liquid phase outlet is connected to the second heat exchange component. The first four-way valve, wherein the first valve port, the second valve port, the third valve port and the fourth valve port of the first four-way valve are respectively connected to the first heat exchange component, the third heat exchange component, the input port and the second heat exchange component; A one-way valve, wherein the inlet of the one-way valve is connected to the second heat exchange assembly, and the outlet of the one-way valve is connected to the first heat exchange assembly, wherein the first heat exchange assembly and the second heat exchange assembly are modular variable flow path parts, and the direction from the inlet to the outlet of the one-way valve is the conduction direction of the one-way valve. When the air conditioner is running in heating mode, the passage from the first valve port to the fourth valve port and the passage from the second valve port to the third valve port in the first four-way valve are opened. When the air conditioner is running in cooling mode, the passage from the first valve port to the third valve port and the passage from the fourth valve port to the second valve port in the first four-way valve are opened.

2. The air conditioner according to claim 1, characterized in that, The first four-way valve is also connected to the compressor's exhaust port or a high-pressure pipeline connected to the exhaust port via a first connecting pipe, and to the compressor's suction port or a low-pressure pipeline connected to the suction port via a second connecting pipe.

3. The air conditioner according to claim 1, characterized in that, Includes at least one of the following: The number of flow path branches in the first heat exchange component is greater than the number of flow path branches in the second heat exchange component; The number of flow path branches in the second heat exchange component is greater than the number of flow path branches in the third heat exchange component.

4. The air conditioner according to claim 3, characterized in that, include: The number of U-tubes in the second heat exchange component and the third heat exchange component is 0.2 to 0.55 times the number of U-tubes in the first heat exchange component; the number of U-tubes in the third heat exchange component is 0.05 to 0.3 times the number of U-tubes in the first heat exchange component and the second heat exchange component.

5. The air conditioner according to claim 1, characterized in that, The first throttling device is one of the following: an electronic expansion valve or a capillary tube.

6. A control method for an air conditioner, characterized in that, The method is applicable to an air conditioner according to any one of claims 1 to 5, wherein the heat exchanger in the air conditioner includes a first throttling device and a first four-way valve, the first four-way valve including a first valve port, a second valve port, a third valve port, and a fourth valve port, and the first throttling device is a first expansion valve, the method comprising: Obtain the heat exchange mode of the air conditioner; According to the heat exchange mode, the conduction state of the first four-way valve and the opening degree of the first expansion valve are controlled.

7. The control method according to claim 6, characterized in that, The heat exchange mode includes a heating mode, and controlling the conduction state of the first four-way valve and the opening degree of the first expansion valve according to the heat exchange mode includes: When the air conditioner is running in heating mode, the passage from the first valve port to the fourth valve port and the passage from the second valve port to the third valve port in the first four-way valve are opened. Obtain the target operating frequency of the compressor, and determine the initial opening degree of the first expansion valve based on the target operating frequency; The evaporation superheat of the heat exchanger is obtained at a first preset time interval, and the target opening degree of the first expansion valve is obtained based on the evaporation superheat; wherein, the evaporation superheat is obtained by subtracting the second temperature value at the compressor suction port from the first temperature value at the heat exchanger.

8. The control method according to claim 7, characterized in that, The step of obtaining the target opening degree of the first expansion valve based on the evaporation superheat includes: The evaporation superheat is compared with at least one preset temperature value, and the opening adjustment value is determined based on the comparison result. The target opening of the first expansion valve is obtained by adding the initial opening to the opening adjustment value.

9. The control method according to claim 6, characterized in that, The heat exchange mode also includes a cooling mode. Controlling the conduction state of the first four-way valve and the opening degree of the first expansion valve according to the heat exchange mode includes: When the air conditioner is running in cooling mode, the passage from the first valve port to the third valve port and the passage from the fourth valve port to the second valve port in the first four-way valve are opened. Adjust the opening of the first expansion valve to its maximum.

10. A controller, characterized in that, The device includes a memory, a processor, and a computer program stored in the memory and executable on the processor, the processor executing the program to implement the control method for an air conditioner as claimed in any one of claims 6 to 9.

11. A computer-readable storage medium, characterized in that, The computer-readable storage medium stores computer-executable instructions for causing a computer to perform the control method for an air conditioner as described in any one of claims 6 to 9.

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